Hydraulic extrusion press



Sheet of '7 a m @E l .R m 0 A :Y. mm m nM 0N" N2 N9 E E 0 mm 0/9 k, mm W m w mm I A i Km 4 1 a I N2 m n M y w mm mm m? u n 0 7 Y B wm wwfi March 11, 1969 Filed Oct. 14, 1964 March 11, 1969 o. 1.. LOMBARD m HYDRAULIC EXTRUSION PRESS Sheet Filed Oct. 14, 1964 INVENTOR.

DANIEL L. LOMBARD ATTORNEY March 11, 1969 D. LOMBARD 3,431,765

HYDRAULIC EXTRUSION PRESS Filed 001. 14, 1964 sheet 3 of '2 V|T 6 I 294 00 3020 INVENTOR' 6 FIG. 7 BY DAN! L L.LQMBARD 4 m7 g I [I 2/? 330 March 11, 1969 o. L. LOMBARD HYDRAULIC EXTRUS ION PRESS Sheet 4- of Filed 001.. 14. 1964 m9 QI INVENTOR.

DANIEL L. LOMBARD ATTORNEY March 11, 1969 o. L. LQMB'ARD HYDRAULIC EXTRUSION PRESS Sheet 6 01? Filed Oct. 14. 1964 FIG. I6

INVENTOR.

DANIEL L. LOMBARD ATTORNEY FIG. 15

March 11,1969 0. L. LOMBARD HYDRAULIC EXTRUSION PR Sheet Filed Oct. 14. 1964 INVENTOR.

DANIEL L LOMBARD Q wE ATTORNEY v United States Patent 3,431,765 HYDRAULIC EXTRUSION PRESS Daniel L. Lombard, Youngstown, Ohio, assignor to Lomlard Corporation, Youngstown, Ohio, a corporation of bio Filed Oct. 14, 1964, Ser. No. 403,836 US. Cl. 72-255 29 Claims Int. Cl. B21c 23/21, 35/04 ABSTRACT OF THE DISCLOSURE This patent discloses a hydraulic extrusion press having certain desirable features. In place of the forged steel columns that are usually used to restrain the forces separating the cylinder and the die, there are used horizontal slab members, which may be substantially unmachined to save expense, and which are keyed to vertical slab members associated with the die and the cylinder. The patent further discloses the press as having a hydraulic cylinder formed of two tubes, one nested within the other, so that it is possible to use appropriately finished heavy-walled tubing rather than a single-Wall cylinder that would need to be specially manufactured. The patent further discloses means for moving the ram associated with the piston rod to a position outboard of the press, to facilitate its replacement; this means comprises a hydraulic cylinder mounted on a carriage pivoted at one end, the other end being movable along an arcuate track from an inoperative position to an operative position. The patent further discloses a billet container adjustable both horizontally and vertically about its operative position and a billet loader movable by means of a pair of coplanar arms operating in a pantograph-like fashion (so that the billet loader is held level during movement) to a position outboard of the press. To facilitate changing of the liner of the billet container, the billet container is also made movable to a position outboard of the press. Means for removing the butt and dummy block and means for changing dies are also disclosed. With the features described, there is provided a press that is versatile and convenient to use, and relatively inexpensive to manufacture.

This invention relates to a hydraulic extrusion press, and more particularly to certain improvements in the construction of horizontal extrusion press installations which have the ultimate effect of simplifying its construction thereby significantly reducing the cost of manufacture and installation.

As is known, a conventional extrusion press construction incorporates a cast steel platen which supports an extrusion die with an adjacent billet container; and a cast steel cylinder housing which supports a cast steel hydraulic cylinder into which is inserted a heavy chill cast iron piston having a ram projecting therefrom toward the billet container. During extrusion of a billet, hydraulic fluid under pressure is introduced into the hydraulic cylinder to force the ram into the billet container. A billet disposed within the container, is extruded through the extrusion die.

During the extrusion operation, tremendous expansive forces are produced which, in the absence of connecting elements, would separate the platen and the cylinder housing. In order to resist these expansive forces, the platen and cylinder housing are connected normally by means of a plurality of forged steel columns which are secured to and extend between the platen and the cylinder housing. The forged steel columns normally are equally spaced about the central axis of the extrusion die. Thus, the expansive forces are transmitted substantially equall to the columns in the form of tensile forces, i.e., the columns are under considerable tension during the actual extrusion operation. For example, extrusion press machinery having capacities of 2000 to 2400 tons are common.

As is known, elements such as the platen and cylinder housing when formed from cast steel are relatively expensive. Furthermore, forged steel columns also are expensive to manufacture. The cost stems not only from the forging operation but also because they require a considerable amount of machining in order that they may be properly assembled to the platen and the cylinder housing. Accordingly, extrusion press facilities have had only limited application, and generall only in the large and well-established manufacturing concerns to whom the expense of extrusion press installation and servicing is a surmountable burden.

As an important overall object, the present invention seeks to provide an extrusion press installation of improved and novel construction whereby such installations are rendered suitable for and economically feasible to smaller manufacturers and fabricators.

More particularly, the present invention seeks to provide a novel extrusion press installation comprising a horizontal extrusion press having improved and substantially simplified press frame and hydraulic cylinder constructions which significantly reduce the cost of fabrication and installation of the extrusion press.

Other important objects of the present invention, include:

To provide an extrusion press having a frame of simplified construction, which is equally as rigid and of equal capacity as those frames manufactured in accordance with conventional designs;

To provide an extrusion press with a frame of improved design which results in a reduction in the overall size of the press frame as compared to an extrusion press of the same capacity incorporating normal design features;

To provide an extrusion press having a hydraulic cylinder formed from two telescoping substantially unmachined tubular members, the construction resulting in a considerably more simplified design and a significant reduction in the cost of manufacture and installation of the same;

To provide a novel extrusion press having a ram supporting structure which is movable laterally of the frame and to a position outboard thereof wherein replacement of the ram is easily accomplished;

To provide a novel extrusion press wherein the billet container is movable transversely of the frame to a position outboard thereof wherein replacement of the billet container is easily accomplished;

To provide a novel extrusion press wherein loading of each billet is accomplished from a position outboard of theframe, which position is easily accessible to the operators;

To provide a novel extrusion press wherein the butt of the extruded billet and the dummy block associated therewith are caught after shearing from the extrusion die and displaced to a position outboard of the frame wherein discharge thereof is easily accomplished; and

To provide 'a novel extrusion press having a plurality of extrusion dies which are alternately positionable in alignment with the billet container for extrusion of a billet.

In accordance with the invention, a horizontal extrusion press is provided having a frame formed from upper and lower horizontal slab members which extend over and under the extrusion press and substantially parallel with the central axis of the extrusion die. First and second vertical slab members comprising a solid-steel platen and a solid-steel crown, each extend vertically between a pair of adjacent ends of the horizontal slab members.

Novel connecting means are employed for connecting the horizontal slab members to the upper and lower ends of the first and second vertical slab members, the arrangement being such that substantially all of the expansive force produced by the extrusion press is transferred to the connecting means in the form of shear forces. The present, connecting means provides a simplified, low-cost method of connecting the horizontal slab members to the first and second vertical slab members. The resulting press frame has the required rigidity and load-carrying capacity.

The upper and lower horizontal slab members, as used in the present invention, require a minimum of machining or preparation. For example, rolled steel slabs in the form in which they leave the roll mill, may be used with a minimum of further preparation. The only machining required is performed on the slab ends, in the region of connection to the first and second vertical slab members. By using steel slabs in this form instead of the previously employed forged steel columns, the cost of fabrication and installation of the press frame and the overall size of the extrusion press are significantly reduced.

Further, in accordance with the invention, there is provided a hydraulic cylinder means of simplified construction and employing a pair of telescoping outer and inner tubular members. In the present hydraulic cylinder means, the second vertical slab member is employed for sealing one end of the outer tubular member while a crosshead, which also supports the ram, is employed to seal the free end of the inner tubular member. A sealing member is interposed between the outer and inner tubular members at the projecting end of the outer tubular member. In the present hydraulic cylinder means, the outer and inner tubular members require a minimum of machining or preparation and, hence, further reduce the cost of fabricating the present extrusion press.

Further, in accordance with the invention, the ram is supported for movement transversely of the frame to a position outboard of the frame whereby replacement of a worn ram is easily accomplished. A novel means is provided for moving the ram between the outboard position and the operative position wherein it is in alignment with the central axis of the extrusion die. The billet container of the present extrusion press, is movable axially along the frame and laterally thereof to a position outboard of the frame. In the outboard position, replacement of a worn billet container may be easily accomplished. In the present extrusion press, unextruded billets are loaded onto a loading mechanism which is disposed outboard of the frame. The loading mechanism then is displaced within the frame proper to position the unextruded billet in alignment with the billet container. Means is provided for catching the butt of the extruded billet and the dummy block associated therewith upon shearing thereof from the extrusion die. The catch means thereafter moves the butt and dummy block to a position outboard of the frame wherein removal is easily accomplished.

The above and other objects and advantages of the present invention will become apparent from the following detailed description by reference to the accompanying drawings, in which:

FIG. 1 is an overall plan view of the present extrusion press;

FIG. 2 is an overall side view of the present extrusion press;

FIG. 3 is a fragmentary cross-sectional view, taken substantially along the line III-'III of FIG. 1, illustrating a means for connecting a horizontal slab member and a vertical slab member;

FIGS. 4 and 5 are fragmentary cross-sectional views, similar to FIG. 3, illustrating alternative connecting means for securing a horizontal slab member to a vertical slab member;

FIG. 6 is a fragmentary side view, with portions cut away to show details, illustrating the main cylinder means for displacing the ram of the present extrusion press;

FIG. 7 is a cross-sectional view, taken along the line VIIVII of FIG. 6, further illustrating the main cylinder means of the present extrusion press;

FIG. 8 is a crosssectional view, taken along the line VIII-VIII of FIG. 1, illustrating a ram supporting structure and means for displacing the same;

FIG. 9 is a cross-sectional view, taken along the line IXIX of FIG. 8, further illustrating the ram supporting structure of FIG. 8;

FIG. 10 is a cross-sectional view, taken along the line XX of FIG. 2, illustrating a billet container supporting assembly;

FIG. 10A is a fragmentary elevation view, on an enlarged scale, illustrating means for displacing the billet container in a horizontal direction;

FIG. 10B is a fragmentary elevation view, on an enlarged scale, illustrating means for elevating and lowering the billet container;

FIG. 11 is a fragmentary side view illustrating the billet contained support platform prior to movement of movement thereof transversely of the press frame;

FIG. 12 is a cross-sectional 'view, taken along the line X IIXII of FIG. 10, illustrating a means for keying the billet container support platform prior to movement to the billet container toward the extrusion die;

FIG. 13 is a fragmentary cross-sectional view, taken along the line XIII-XII-I of FIG. 1, illustrating a billet loading mechanism;

FIG. 14 is a side view further illustrating the billet loading mechanism of FIG. 13:

FIG. 15 is a cross-sectional view, taken along the line XV-XV of FIG. 1, illustrating a butt and dummy block catching mechanism;

FIG. 16 is a side view of the butt and dummy block catching mechanism of FIG. 15;

FIG. 17 is a cross-sectional view, taken along the line XVII-XVII of FIG. 2, illustrating a multiple extrusion die supporting assembly;

FIG. 18 is a plan view as seen from the line XVIII XVIII of FIG. 17, illustrating a clevis connecting arrangement between the die slide plate and a power means;

FIG. 19 is a cross-sectional view, taken along the line XIXXIX of FIG. 18, further illustrating the clevis connecting means; and

FIG. 20 is a cross-sectional view, taken along the line XX-XX of FIG. 17, illustrating one of the extrusion die assemblies employed in the present extrusion press.

EXTRUSION PRESSGENERAL DESCRIPTION Reference is now directed to FIGS. 1 and 2, wherein there is illustrated a horizontal extrusion press generally designated by the numeral 30. The extrusion press 30 is adapted to rest on a horizontal surface and comprises a frame 32 formed from upper and lower horizontal slab members 34, 36 and first and second vertical slab members 38, 40. The press frame 32 is closed at both ends and at its top and bottom. Entrance to the interior of the press frame 32 is provided only through its opposite sides. Connecting means 42 are provided for securing the first and second vertical slab members 38, 4G to the upper and lower horizontal slab members 34, 36.

The first vertical slab member 38 is provided with an opening 44 (shown in phantom outline) through which will extend the extruded product. Mounted on the inner face of the first vertical slab member 38, is an extrusion die structure 46 which, as will be described, includes two spaced-apart extrusion die assemblies which are alternately positionable in alignment with the opening 44 of the first vertical slab member 38. Adjacent to the extrusion die structure 46 is a billet container 48 which receives a billet 50 and associated dummy block 52 (both shown in dotted outline) and supports the same in alignment with the die opening of the extrusion die structure 46.

Projecting axially toward the extrusion die structure 46 is a. main hydraulic cylinder means 54 which is supported on the second vertical slab member 40. A main hydraulic cylinder means 54 includes a piston 56 which is forcibly moved toward the extrusion die structure 46 by means of hydraulic fluid under pressure. Hydraulic fluid pumping apparatus 58 is supported on the upper horizontal slab member 34 adjacent to the hydraulic cylinder means 54. A conduit 60 depends vertically from the pumping apparatus 58 along with additional piping, and serves to communicate the hydraulic fluid through a valve 62 into the hydraulic cylinder means 54 during the extrusion operation. A pumping apparatus and valve suitable for use in the present extrusion press are disclosed and illustrated in U.S. Patent No. 2,751,076.

At the free end of'the piston 56 there is supported a ram 64 which, during the extrusion operation, enters the billet container 48 and forces the billet 50 to be extruded through the die opening provided in the extrusion die structure 46. At the completion of the extrusion operation, the piston 56 will project out of the hydraulic cylinder means 54. The piston 56 is retracted within the hydraulic cylinder means 54 by means of a pair of piston motor means 66 disposed on opposite sides of the cylinder means 54.

At the completion of the extrusion of one billet, the billet container 48 must be moved away from the extrusion die structure 46 so that the remaining portion of the billet 50, hereinafter to be termed butt, and the dummy block 52 may be removed from the extrusion die structure 46. The billet container 48 is supported for movement toward and away from the extrusion die structure 46 by me.ns of first track means 68-. The billet container 48 is moved by means of a pair of container motor means 70, each of which preferably comprises a hydraulically operated cylinder having a piston rod 72, the end of which is releasably secured to the billet container 48. Activation of the pair of container motor means 70 will cause the billet container 48 to be moved away from the extrusion die structure 46 into the position indicated at dotted outline at 48' (FIG. 2). At this time a butt and dummy block catch mechanism 74 (FIG. 1) will be activated to introduce a catching member between the billet container 48 and the extrusion die structure 46. Thereafter, a butt shear mechanism 76 will lower a butt shear 77 carried thereon, between the billet container 48 and the extrusion die structure 46 to shear the butt and dummy block from the extrusion die structure 46. The catching member of the butt and dummy block catch mechanism 74 receives the butt and dummy block and transports them to a posi tion. outboard of the frame 32 wherein they may be unloaded.

'Ihe extrusion die structure 46 includes motor means (to be described in conjunction with FIG. 17) whereby the die structure 46 may be shifted to the right or to the left to align a new extrusion die assembly with the opening 44 and the billet container 48. The previously employed extrusion die assembly, which now resides at a position outboard of the frame 32, will be disengaged from the die structure 46. Die knockout means 78a, 78b, one each disposed on each side of the frame 32, are employed to push the extrusion die assembly out of the die structure 46, as will be described.

Reactivation of the container motor means 70 will move the billet container 48 toward the extrusion die structure 46 in the position illustrated in FIG. 2. At this time a new billet 50 may be loaded into the billet container 48. A billet loading mechanism 80 (FIG. 1) having a cradle which normally is disposed in a position outboard of the frame 32, is provided to transfer a new billet 50 and dummy block 52 into axial alignment with the central axis of the extrusion die and adjacent to the front face of the billet container 48 as shown in FIG. 2. At this point, the hydraulic cylinder means 54 will be activated whereby the ram 64 will displace the new billet 50 and dummy block 52 into the billet container 48 preparatory to extr'uding the same.

After a series of billets have been extruded, the ram 64- normally must be replaced. In the present extrusion press 30, the ram 64 is supported for sliding movement transversely of the frame 32 from an operative position wherein the ram 64 is in axial alignment with the central axis of the extrusion die to a second position wherein the ram 64 is disposed outboard of the frame 32. In the outboard position, exchange of the ram 64 may be relatively easily accomplished. Movement of the ram 64 to the outboard position is accomplished by means of a ram motor means 82. The ram motor means 82 is mounted for gate-like movement from an inoperative position shown in full lines in FIG. 1 to an operative'position shown in dotted lines. In the operative position, the ram motor means 82 extends perpendicularly to the frame 32 and is aligned with the ram supporting structure. The ram motor means 82 preferably comprises a hydraulically operated cylinder and piston having a piston rod 84 which, when the ram motor means 82 is in the operative position, may be extended into coupled engagement with the ram supporting structure and retracted for transporting the ram 64 to the aforementioned out-board position. When the exchange of the ram has been accomplished, the ram motor means 82 is activated to push the ram supporting structure into the frame 32 whereby the new ram is axially aligned with the central axis of the die. The piston rod 84 is disconnected from the ram supporting structure and is retracted. Thereafter, the ram motor means 82 is swung to the inoperative position shown in full lines in FIG. 1. After a series of billet-s have been extruded, it is nonm-al to replace a liner housed within the billet container 48. The liner receives and supports the billet 50 during extrusion thereof. To exchange the liner, the billet container 48 first is moved away from the extrusion die structure 46 by means of the pair of container motor means 70. At this point, the piston rods 72 of the container motor means 70 are detached from the billet container 48 and retracted. As can best be seen in FIG. 2, the first track means 68 is supported on a platform 86 which, in turn, is supported for sliding movement transversely of the press frame 32 by means of second track means 88. The second track means 88 extend outboard of the frame 32 (see FIG. 1). Secured to and disposed on the opposite side of the platform 86 is a platform motor means 90 which serves to move the platform 86 together with the billet container48 to a position outboard of the frame 32. In this outboard position, the liner may be replaced. Thereafter, the platform motor means 90 is reactivated to move the platform 86 and the billet container 48 into the frame 32 and position it in axial alignment with the central axis of the extrusion die. The piston rods 72 of the container motor means 70 are extended and again secured to the billet container 48. Activation of the container motor means 70 now will move the billet container 48 along the first track means 68 to a position adjacent to the extrusion die structure 46 as illustrated in FIG. 2.

PRESS FRAME 32.

The press frame 32 is of simplified construction wherein the cost of manufacturing the same is significantly reduced. Although the press frame is of simplified construction, its rigidity and load-carrying capacity are equal to those of press frames manufactured in accordance with conventional design practices. The upper and lower horizontal slab members 34, 36 comprise solid-steel slabs which are substantially unrnachined. Similarly, the first and second vertical slab members 38, 40 comprise solidsteel slabs which are substantially unmachined. In essence, then, the slabs 3440 may be used substantially in the form in which they leave the roll mill, i.e., with a minimum of further preparation. The only machining required in these slabs is performed on the ends, in the region of con- 7 nection between the horizontal slab members 34, 36 and the vertical slab members 38, 40.

The preferred construction of the connecting means 42 is illustrated in FIG. 3 on an enlarged scale. The connecting means 42 are identical in construction, hence, only one of the connecting means 42 will be described. As can be seen in FIG. 3, a groove 92 is formed in the lower face 94 of the slab member 34 adjacent to the end thereof. The groove 92 extends transversely of the slab 34 and is adapted to receive an upper end portion 95 of the vertical slab member 38. The groove 92 is wider than the vertical slab member 38. A pair of claming members 96, one each on each side of the vertical slam member 38 serve to clamp the slab member 38 to the horizontal slab 34, thereby preventing vertical separation thereof during the extrusion of a billet. Each of the clamping members 96 is interposed between one side of the vertical slab member 38 and a vertically disposed wall of the groove 92. Each of the clamping members 96 includes a lug 98 engaged in a slot 100 formed in each side wall of the vertical slab 38. A plurality of bolts 102 (only one visible) extends through the clamping member 96 and is threaded into the horizontal slab 34.

During the extrusion of a billet, a portion of the expansive force produced by the extrusion press 30 will tend to move the vertical slab member 38 in the direction of the arrow 104. This force will be resisted by a tensile force acting on the horizontal slab 34 and indicated by the arrow labeled T. From the principles of statics, the forces acting on the end portion 95, which in reality is a key, are substantially entirely shear forces. Hence, in the press frame 32, the connecting means 42 are positioned to resist substantially all of the expansive forces produced in the extrusion press 30. The expansive forces are applied to the connecting means 42 as shearing forces.

An alternative configuration of a connecting means is illustrated in FIG. 4 and indicated by the numeral 106. Corresponding primed numerals will be employed to identify corresponding parts already described. In this configuration, the horizontal slab 34' includes a depending lug or rib 108 which resides within a groove 110 formed in the upper end of the vertical slab member 38. A plurality of bolts 112 secures the horizontal slab 34' to the vertical slab 38 and prevents their vertical separation during an extrusion operation. An analysis of this configuration with respect to the forces acting on the lug 108 will reveal that the lug 108 is being acted on by shearing forces. The lug 108 and the groove 110 extend transversely of the horizontal slab 34 and the vertical slab 38, respectively, and along substantially the entire length thereof. Hence, the connecting means 106 is positioned to resist substantially all of the expansive forces produced by the extrusion press 30 as shear forces.

A further alternative configuration of a connecting means is illustrated in FIG. and is indicated generally by the numeral 114. Corresponding double primed numerals will be employed to identify parts already described. As can be seen in FIG. 5, the vertical slab member 38" includes a keyway 116 formed in its upper face 118. The horizontal slab member 34" includes a lower face 120 which is engaged with the upper face 118 of the vertical slab member 38 and which has a keyway 122 formed therein. The keyway 122 corresponds with the keyway 116. Residing within the corresponding keyways 116, 122 is an extrinsic shear key 124. A plurality of bolts 125 prevents vertical separation of the horizontal slab member 34" and the vertical slab member 38" during operation of the extrusion press 30. The corresponding keyways 116, 122 and the shear key 124 extend transversely of the horizontal slab member 34 and along substantially the entire width of the horizontal slab member 34 and the vertical slab member 38". Hence, during the extrusion of a billet, the shear key 124 will sustain the expansive forces produced in the extrusion press 30 as shearing forces.

8 MAIN HYDRAULIC CYLINDER 54 For a complete description of the main hydraulic cylinder means 54, reference is directed to FIGS. 2, 6 and 7. The hydraulic cylinder means 54 and piston 56 preferably comprise a pair of telescoping outer and inner tubular members 126, 128. The outer tubular member 126 has an inside diameter which is larger than the outside diameter of the inner tubular member 128. The outer tubular member 126 projects horizontally from and has one end secured to the second vertical slab member 40. The second vertical slab member 40 is provided with a passageway 130 which serves to communicate the hydraulic fiuid under pressure into the interiors of the first and second tubular members 126, 128 during the extrusion operation. The first tubular member 126 is supported at its other end by means of a plurality of brace members 132 which support the first tubular member 126 at spaced points around its periphery. The brace members 132 are secured to the upper and lower horizontal slab members 34, 36.

The inner tubular member 128 is slideably supported within the outer tubular member 126 by means of suitable sealing means 134 and bushing 136. The sealing means 134 and bushing 136 are disposed in the annular space between the outer and inner tubular members 126, 128. The inner tubular member 128 is slideable through the sealing assembly 104 and the bushing 136 toward and away from the billet container 48. Thus, the outer surface of the inner tubular member 128 must be finished to prevent injury to the components of the sealing means 134 and to reduce the sliding friction between the sealing means 134 and the bushing 136. It should be noted that only a portion of the inner surface of the outer tubular member 126 and the outer surface of the inner tubular member 128 require a finishing operation. Hence, the outer and inner tubular members 126, 128 may comprise substantially unmachined large diameter pipe sections having mechanical properties such as tensile strength and allowable stress values in excess of the forces under which they will be subjected.

Secured across the outer end of the inner tubular member 128 is a crosshead 138 which serves to seal the outer end of the inner tubular member 128 and also to support the ram 64. As can be seen in FIG. 2, the crosshead 138 is supported on track members 140 (one visible) for sliding movement toward and away from the billet container 48. The piston motor means 66, employed in retracting the inner tubular member 126, each comprise a hydraulically operated cylinder having a piston rod 142 secured to the crosshead 138. It should be evident, then, that a significant reduction in the cost of fabricating the hydraulic cylinder means 54 is achieved through the use of substantially unmachined telescoping tubular members.

SUPPORTING STRUCTURE AND REPLACEMENT OF RAM 64 As stated above, the ram 64 is supported on the crosshead 138 for movement transversely of the press frame 32 from an operative position, illustrated in FIG. 2, wherein the ram 64 is aligned with the central axis of the die, to a replacement position wherein the ram 64 is disposed outboard of the press frame 32. A complete description of the supporting structure and means for moving the ram between the operative and inoperative positions will now be described with reference to. FIGS. 1, 2, 8 and 9.

As can best be seen in FIG. 9, the ram 64 has an enlarged end portion 144 which is received within a correspondingly shaped opening 146 provided in a slide plate 148. A stop member provided at one side of the crosshead 138 is engaged by the slide plate 148 to position the ram 64 in axial alignment with the central axis of the die. A locking pin 152 extends through the stop member 150 and the slide plate 148 to lock the slide plate 148 in the operative position.

As can be seen in FIGS. 2 and 8, the slide plate 148 is clamped to the crosshead 138 and supported for sliding movement by a pair of clamping members 154. Extraction of the locking pin 152 and loosening of the clamping members 154 permits the slide plate 148 to be moved transversely of the press frame 32 to an inoperative position illustrated in dash-dot outline in FIG. 8. In the inoperative position, the ram 64 is disposed outboard of the press frame 32 wherein replacement thereof is easily accomplished.

As described above in conjunction with FIG. 1, the ram motor means 82 may be moved in gate-like fashion from the inoperative position shown in full lines to the operative position shown in dotted outline in FIG. 1. In FIG. 8 the ram motor means is shown disposed in its operative position. The ram motor means 82 is supported on a carriage 156. A vertically oriented pivot means 158 is connected to and supports one end of the carriage 156 whereby the carriage 156 may be swung in gate-like fashion. The opposite end of the carriage 156 is provided with a roller 160 which rolls over a length of arcuate track member 162, best seen in FIG. 1, between the inoperative and operative positions described above. A pin member 164 extends through a bracket 166 and into a plate 168 of the carriage 156 to lock the ram motor means 82 in its operative position during transfer of the slide plate 148 and ram 64.

When replacement of the ram 64 is required, the ram motor means 82 is swung into its operative position illustrated in FIG. 8 and locked therein. The piston rod 84 is then extended toward the slide plate 148. As can be seen in FIGS. 8 and 9, the remote end of the piston rod 84 is provided with a coupling member 170' which fits into an opening 172 provided in the slide of the slide plate 148. A locking pin 174 extends through slide plate 148 and the coupling member 170 to complete the securement of the remote end of the piston rod 84 to the slide plate 148. Thereafter, the ram motor means 82 may be reactivated to pull the slide plate 148 to the outboard position illustrated indash-dot outline in FIG. 8. After a new ram has been installed in the slide plate 148, the ram motor means 82 is activated to move the slide plate 148 into the operative position, illustrated in full lines in FIG. 8. The slide plate 148 then is locked in position by means of the locking pin 152. Extraction of the locking pin 174 permits retraction of the piston rod 84. Thereafter, the locking pin 164 may be extracted and the carriage 156 moved so that the ram motor means 82 is in its inoperative position shown in full lines in FIG. 1.

BILLET CONTAINER 48 Referring to FIGS. and 11, the billet container 48 comprises a housing 176 formed from upper and lower housing portions 178a, 1781). Within the housing 176 there is secured a liner 180 having a billet receiving opening 182 provided centrally therein. The upper housing portion 178a is detachable from the lower housing portion 17811 whereby the liner 180 may be replaced when worn.

The container motor means 70 are disposed on opposite sides of the billet container 48 in diametrically opposed relation. The arm structures are each provided with a rod receiving conduit 186 (FIG. 11) which receives the piston rod 72 of each of the container motor means 70. The piston rod 72 is releasably secured to the arm structures 184, for example, by means of a split-body collar 188. The collars 188 permit extraction of the piston rod 72 from the rod receiving conduits 186 whereby the billet container 48 may be moved laterally of the press frame 32 for exchange of the liner 180, as will be described.

In FIG. 10 there is shown a hydraulic cylinder 190 having a cradle 192 supported for movement into axial alignment with the billet receiving opening 182. The cradle 192 is adapted to support an ejector block 193 which is inserted within the billet receiving opening 182 for the purpose of cleaning it out. The ejector block 193 is forced through the billet receiving opening 182 by means of the ram 64.

As stated above, the billet container 48 is movable axially of the press frame 32, that is, parallel with the central axis of the die opening; and also is movable transversely of the press frame 32 to position the billet container outboard of the press frame 32 for the purpose of exchanging the liner 180. In FIG. 11, the billet container 48 is shown spaced from the extrusion die structure 46 (shown in dash-dot outline). The billet container is dis placed into this position so that the liner may be cleaned by forcing the ejector block 193 through the billet receiving opening 182 thereof; and to permit shearing of a butt 194, shown in dash-dot outline, from the extrusion die structure 46 by means of the butt shear mechanism 76 shown in FIG. 2. The butt 194 comprises that portion of the billet 50 which remains at the completion of the extrusion operation. Notice also that the dummy block 52 remains engaged with the butt 194.

The billet container 48 is movable along the first track means 68 from a position adjacent to the extrusion die structure 46, as shown in FIG. 2, to a position spaced from the extrusion die structure 46, as illustrated in FIG. 11. As can be seen in FIGS. 10 and 108, each of the first track means 68 comprises a wear plate 196 supported on and secured to an inclined plate 198. A liner 200 is secured to a shoe 202 and is engaged over the wear plate 196. A second shoe 204 is disposed above the shoe 202 and is engageable in a groove 206 formed in avbearing plate 208. The second shoe 204 is slideable to the right and to the left of FIG. 10B within the groove 206. The first and second shoes 202, 204 are maintained spaced apart and coupled by means of a rod 210 residing in corresponding grooves formed in the opposed faces of the first and second shoes 202, 204. The rod 210 permits the second shoe 204 to undergo tilting movement about the rod 210 while the liner 200 is maintained in surface engagement with the wear plate 196. As is known, the billet container 48 will be heated by means (not shown) as well as by introduction of a hot billet. The upper portion of the billet container 48 will tend to expand at a greater rate than the lower portion. Consequently, the uneven expansion occurring in the billet container 48 will cause the bearing plates 208 to undergo tilting in opposite directions. Since the rod 210 permits the second shoe 204 to undergo slight tilting movement, the tilting of the bearing plates 208 will not affect the position of the first shoe 202 whereby the liner 200 is maintained in overall surface engagement with the wear plate 196. Hence, the first and second shoes 202, 204 and the rod 210 comprise means for maintaining the liner 200 in overall surface contact with the bearing plate 196 and for compensating for the skewing of the bearing plates 208 caused by the uneven expansion of the billet container 48.

It is necessary that the central axis of the billet receiving opening 182 be coaxial with the central axis of the die opening. Hence, as can be seen in FIG. 10, the billet container 48 is provided with a vertical adjustment means 212, one each associated with each of the first track members 68, and a horizontal adjustment means 214 disposed centrally between the track means 68.

The vertical adjustment means 212 is best illustrated in FIG. 10B. As can be seen therein, a flange 216 depends from the outboard end of the bearing plate 208 and receives a plurality of adjusting bolts 218, the inner ends of which engage the first shoe 202. Inward movement of the adjusting bolts 218 will cause the first and second shoes 202, 204 to undergo simultaneous inward and upward movement. That is to say, the first shoe 202 will slide up the inclined plate 196 While the second shoe 204 will slide horizontally across the groove 206. Movement in the inward direction will cause the billet container 48 to be raised so as to'elevate the central axis of the billet receiving opening 182. Conversely, outward movement of the adjusting bolts 218 will cause the billet container 48 to be lowered.

The horizontal adjustment means 214 is best illustrated in FIG. A. The horizontal adjustment means 214 comprises a vertical bearing member 220 which projects above the platform 86 and extends parallel to the central axis of the extrusion die. Disposed on each side of the vertical bearing member 220 are cup-like members 222 which are secured to the lower face of the lower housing portion 1781). The cup-like members 222 each threadeclly receive a plurality of adjusting bolts 224. On the lower legs of the cup-like members 222 there is supported a wear plate 226 each disposed in surface engagement with the lateral surfaces of the vertical bearing member 220. In FIG. 10A, the billet container 48 is movable into and out of the plane of the drawing. During this movement, the billet container 48 will be guided by the wear plates 226 and the vertical bearing member 220. The billet container 48 may be disposed in a horizontal direction, for example,

to the right of FIG. 10A, by loosening those adjusting bolts 224 on the right side of the bearing member 220 and by tightening those adjusting bolts 224 on the left side of the bearing member 220. Conversely, loosening of the adjusting bolts on the left-hand side of the bearing member 220 and tightening of the adjusting bolts 224 on the right-hand side of the bearing member 220 will cause the billet container 48 to be displaced to the left of FIG. 10A.

Referring now to FIGS. 10 and 11, the billet container 48 may be moved to a position outboard of the press frame 32 wherein replacement of the liner 180 may be accomplished. During lateral movement of the billet container 48, the platform 86 slides over the second track means 88 which extends over the lower horizontal slab member 36 and laterally thereof. The platform motor means 90 when activated, will displace the billet container 48 and the platform 86 over the second track means 88. After the liner 180 has been replaced, and the upper housing portion 178a has been secured to the lower housing portion 178b, the platform motor means 90 is activated to move the billet container 48 and the platform 86 to the right of FIG. 10. Unitary stop and locking means 228a, 228b are provided at each end of the platform 86 to terminate the movement of the platform 86 when the central axis of the billet receiving opening 182 is aligned with the central axis of the die opening and to lock the platform 86 in that position.

Each of the unitary stop and locking means 228a, 228b comprises upper and lower cooperating block members 230, 232. As schematically illustrated in FIG. 12, each of the lower block members 232 is provided with a V-shaped groove 234 which is adapted to receive a depending plate portion 236 provided on each of the upper block members 230. The depending plate portion 236 has a peripheral shape which corresponds to the V-shape of the groove 234. In FIG. 12, the platform 86 is illustrated in dotted-outline as being displaced laterally of the lower horizontal slab member 36. The depending plate portions 236 also are shown displaced. It should be evident from FIG. 12 that when the platform 86 is moved over the lower slab member 36, that is, into the position shown in FIG. 10, the depending plate portions 236 of the upper block members 230 will enter the V-shaped grooves 234 of the lower block members 232 until the vertical walls thereof engage the vertical walls of the V-shaped groove 234. At this time, no further inward movement of the platform 86 is possible. Simultaneously, the platform 86 will be locked or fixed to the lower slab member 36 whereby the billet container 48 now may be moved toward the extrusion die structure 46 (FIG. 11).

BILLET LOADING MECHANISM 80 Referring now to FIGS. 1, 13 and 14, the billet loading mechanism 80 comprises a cradle 238 adapted to support a billet 50 in a horizontal position. The cradle 238 is supported by means of a swing frame 240 formed from pairs of coplanar arms 242. The arms of each pair of coplanar arms 242 are pivotally secured at their lower ends to the cradle 238 and are pivotally secured at their upper ends. to a carriage 244. Hence, each pair of arms 242, the cradle ends and the carriage ends cooperate to define a pantograph-like structure wherein the cradle 238 is always horizontal.

The carriage 244 is slideably supported on rods 246 for reciprocal movement parallel to the central axis of the extrusion die. The rods 246 are secured to the upper horizontal slab member 34 by means of plate members 248. A hydraulic cylinder means 250 is pivotally supported at 252 on the carriage 244. The hydraulic cylinder means 250 includes a piston rod 254, the free end of which is pivotally secured as at 255 to the swing frame 240. The overall arrangement of the billet loading mechanism 88 is such that the cradle 238 may be moved through an arcuate path from an unloading position indicated by the arrow designated U to a loading position shown in dotted outline in FIG. 13 by the arrow designated L. The construction of the swing frame 240 is such that the cradle 238 will be maintained in a horizontal position at all times during its movement between the loading position and the unloading position. The hydraulic cylinder means 250 serves to move the swing frame and hence the cradle 238 between the loading and unloading positions.

The cradle 238, the swing frame 240 and the hydraulic cylinder means 250 are suspended from the carriage 244 and are movable therewith along the rods 246. On one side of the carriage 244 there is provided a depending plate member 256 comprising one side of the carriage 244. Secured to the lower end of the depending plate member 256 is a block member 258 having a groove 260 formed therein which opens toward the billet container 4 8. The groove 260 receives a tongue-like member 262 which, as can best be seen in FIG. 10, is secured to and projects above the lower housing portion 178b of the billet housing 176. The connection provided by the groove 260 and tongue 262 permits the billet loading mechanism to be moved with the billet container 48 toward and away from the extrusion die structure 46 thereby maintaining the billet loading mechanism '80 properly aligned with the billet receiving face of the billet container 48. That is to say, at all times during the movement of the billet container toward or away from the extrusion die stnucture 46, the billet loading mechanism 80 will be positioned for loading of a billet into the billet receiving opening 182 of the liner 180. The connection provided by the groove 260 and the tongue 262 also permits the billet container 48 to be moved laterally of the press frame 32 to the aforementioned outboard position without the need for manually disconnecting the billet loading mechanism 80 and the billet container 48. Conversely, upon movemnt of the billet container 48 toward the billet loading mechanism 80, the billet container 48 will be automatically connected to the billet loading mechanism 80 and is movable therewith.

BUTT AND DUMMY BLOCK CATCH MECHANISM 74 As stated above in conjunction with FIG. 11, at the completion of the extrusion of a billet, the billet container 48 is moved away from the extrusion die structure 46 to expose the butt 194 and the dummy block 52. The butt shear mechanism 76 (FIG. 2 is activated to lower the butt shear 77 to shear the butt 194 from the extrusion die structure 46. The butt and dummy block catch mechanism 7 4 is provided for catching the butt 194 and dummy block 52 after shearing thereof and for transferring the same to a position outboard of the press frame 32 wherein removal thereof may be easily accomplished.

Referring now to FIGS. 15 and 16, the butt and dummy block catch mechanism 74 comprises a swing arm 264- having its upper end pivotally connected as at 266 between. a pair of depending flange member 268 which are secured tothe upper horizontal slab member 34. A generally U- shaped catch member 270 is secured to the lower end of the swing arm 264. A hydraulic cylinder 272 is pivotally supported as at 274 between a pair of flange members 276 (only one visible) which extends outwardly from the depending flange members 268. The hydraulic cylinder means 272 includes a piston rod 278 having a clevi smember 280 for pivotally connecting the piston rod 278 to the swing arm 264.

The hydraulic cylinder 272 will effect movement of the swing arm 264 between a loading position shown in full lines in FIG. 15 and an unloading position shown in dashdot outline in FIG. 15. The swing arm. 264 will be moved into the region between the extrusion die structure 46 and the billet container 48 is shown in FIG. 16. The generally U-shaped catch member 270 will be disposed directly beneath the butt 194 and dummy block 52 preparatory to catching the same. The butt shear mechanism 76 upon activation will lower the shear 77 from its normally elevated position illustrated in full lines in FIG. 16 to the limit of its downward stroke as illustrated in full lines in FKIG. 15. During the downward movement, the shear 77 will engage the butt 194 and shear it from the extrusion die structure 46. Upon shearing, the butt 194 and dummy block 52 will fall into the catch member 270, whereupon the hydraulic cylinder means 272 will be activated to transfer the butt 194 and dummy block 52 to a position outboard of the press frame 32 as shown in FIG. 15. In the outboard position of the butt and dummy block catch mechanism 74, the butt 194 and dummy block 52 may be unloaded from the catch member 27 0.

BUTT SHEAR MECHANISM 76 Referring now to FIG. 17, the butt shear mechanism 76 comprises a hydraulic cylinder 282 extending above and secured to the upper horizontal slab member 34. The hydraulic cylinder 282 includes a piston rod 284 to which is attached the shear 77. On opposite sides of the hydraulic cylinder 282 and the piston rod 284 there are provided guide rods 286 which extend through guide conduits 288 secured to the upper horizontal slab member 34. Connecting arm 290 extends between and is connected to the lower ends of the guide rods 286. The lower end of the piston rod 284 also is secured to the connecting arm 290. The overall arrangement is such that When the hydraulic cylinder 282 is activated, the piston rod 284 will be lowered from its normally elevated position illustrated in FIG. 17 to a point below the die opening of the extrusion die structure 46 as illustrated in FIG. 15. Thereafter, the hydraulic cylinder 282 will be reactivated to raise the piston rod 284 into its normally illustrated position. The guide rods 286 and connecting arm 290 serve to guide the piston rod 284 during its downward and upward movement.

EXTRUSION DIE STRUCTURE 46 Referring again to FIG. 17, the extrusion die structure 46 as well as the knockout means 78 now will be described in detail.

The extrusion die structure 46 comprises, in general, a slide plate 292 which is supported on the first vertical slalb member 38 for sliding movement transversely there of by means of upper and lower guide tracks 294, 296. Slide plate motor means 298 disposed below the slide plate 292 serves to move the slide plate transversely of the press frame 32. The slide plate 292 is provided with a pair of generally U-shaped wells 300, one each adjacent each end thereof. Extrusion die assemblies 302a, 30% are provided, one each being received in the wells 300. As will be described, each of the extrusion die assemblies 302a, 302b, includes a tool stack 304 provided with a die-plate 306. The slide plate 292 is provided with a centrally located cold billet removal opening 308. Prior to removing the cold billet from the billet receiving opening 182 of the liner 180, the slide plate 292 is moved so as to align the cold billet removal opening 308 with the billet receiving opening 182 and opening 44 through which the cold billet is removed by the advancing ram 64.

Referring now to FIGS. 17 and 20, each of the extrusion die assemblies 302a, 302b, each comprise a sandwich-like structure including the tool stack 304 and a pair of bolster plates 310, 312. The tool stack 304 is comprised of a housing 314 Within which resides the die plate 306 and a supporting plate 316 to which the die plate is keyed. The tool stack 304 is maintained within the well 300 and releasably secured to the slide plate 292 by means of a tool stack clamp member 318 (FIG. 17). The die plate 306 is provided with a. die opening 320 through which the billets will be extruded. The support plate 316 and the two bolster plates 310, 312 are provided with openings of increased diameter through which the extruded shape will pass. The opening 44 provided in the first vertical slab member 38 is coaxially aligned with these openings and receives the extruded shape. As can best be seen in FIG. 17, the bolster plates 310, 312 are secured within the well 300 by means of a bolster plate clamp member 322 which is secured to the slide plate 292.

At the completion of an extrusion operation, the slide plate motor means 298 is activated to transfer the slide plate from the position shown in full lines in FIG. 17 to the right of FIG. 17 whereby the previously employed extrusion die assembly 302a is now disposed outboard of the press frame 32 and directly above the knockout means 78. To discharge the extrusion die assembly 302a, the clamp member 318 is released whereupon the knockout means 78a is activated. Each of the knockout means 78a, 78b preferably comprises a hydraulically operated cylinder means 32-4 having a piston rod 326 extending vertically toward the extrusion die assembly 302. The slide plate 292 is provided with an opening 328 which is disposed directly beneath the tool stack 304. The opening 328, for example, of the die assembly 302a shown in dotted outline in FIG. 17, is aligned with and receives the piston rod 326 upon activation of the knockout means 78a. The piston rod 326 will engage and displace the tool stack 304 from within the well 300. Thereafter, a new tool stack may be inserted within the well 300 and the clamping member 318 clamped to the slide plate 292.

In FIG. 20 the butt 194, the dummy block 52 as well as an extrusion 329 are illustrated in dotted outline. The dummy block 52, the butt 194 and the extrusion 329 are illustrated in the position they would assume at the completion of an extrusion operation.

At this time, the billet container 48 will be moved away from the extrusion die structure 46 to expose the dummy block 52 and butt 194 for shearing by the butt shear mechanism 76, as described above. It should be noted that'the extrusion die structure 46 and the first vertical slab member 38 are arranged such that two subsequent shearing operations are performed which aid in the clean-out of the opening 44 through which the extrusion 329 is discharged, as well as the clean-out of the bolster plates 310, 312 and the tool stack 304. These shearing operations now will be described.

The first shearing operation occurs when the extrusion ldie structure 46 is shifted to align the cold Ibillet removal opening 308 (FIG. 17) with the opening 44 (FIG. 20). During this shifting, the extrusion 329 is sheared as the bolster plate 312' passes the opening 44. Hence, the extrusion 329 is freed and may be transported away from the extrusion press 30 for storage or further processing.

The second shearing operation occurs when the tool stack 304 is displaced upwardly out of the well 300. During discharge of the tool stack 304, any portion of the extrusion 329 remaining within the support plate 316 and the bolster plate 310 will be sheared. The bolster plate clamp member 322 (FIG. 17) is of substantial size and strength and maintains the bolster plates 310, 312 rigidly fixed within the well 300 during the shearing action. Hence, the bolster plates 310, 312 may be easily cleaned out prior to introducing a new tool stack 304 into the vacant well 300.

As can best be seen in FIG. 17, the slide plate motor means 298 comprises a piston rod 330 and a piston 332 which is housed within a bore 334 formed in the lower track member 296. Openings 336a, 33Gb serve to communicate a working fluid to the opposite sides of the piston 332. At the free end of the piston rod 330 there is secured a connecting block 338 which extends upwardly therefrom. At the upper end of the connection block 338 there is provided a connecting rod 340 which extends inwardly toward the slide plate 292. A connecting block 342 serves to secure the connecting rod 340 to the slide plate 292 in a particular manner which will be described in conjunction with FIGS. 18 and 19. In operation, fluid under pressure is admitted through the opening 336a to force the piston 332 to the right of FIG. 17. The slide plate 292, connected to the piston rod 330, also is moved to the right of FIG. 17. Limit switches (not shown) are provided for stopping the slide plate 292 so that either one of the extrusion die assemblies 302a, 302k or the clean-out opening 308 may be aligned with the opening 44.

As is conventional, the slide plate 292 rides over bronze wear strips or other similar means, from one side of the extrusion press to the other. Cam means (not shown) are provided for adjusting the slide plate 292 to compensate for wear occurring in the aforementioned wear strips. Cam means suitable for use with the present slide plate 292 is illustrated and described in U.S. Patent No. 2,960,202, issued to Daniel A. Katko and assigned to the assignee of the present invention. Hence, the slide plate 292 will be elevated, from time-to-time, through incremental distances to compensate for the wear occurring in the aforesaid wear plates.

The manner in which the second connecting block 342 is connected to the slide plate 292 permits the slide plate 292 to be elevated through incremental distances without affecting the interconnection. Referring now to FIGS. 18 and 19, the end of the second connecting block 342 is provided with a shaft 344 having a disc 346 extending transversely thereof. The shaft 344 and the disc 346 are received within a T-shaped slot 348 formed in the outboard end of the slide plate 292. The shaft 344 and the disc 346 are initially positioned above the lower walls 350, 352 of the T-shaped slot 348. Hence, a space is pro- 'vided through which the slide plate 292 may be moved vertically during adjustments performed by the aforementioned cam means. The shaft 344 and disc 346 and the T-shaped slot 348 provide a clevis-like arrangement.

Although the invention has been illustrated in connection with one specific embodiment, it will be readily apparent to those skilled in the art that various changes in form and arrangement of parts may be made to suit requirements without departing from the spirit and scope of the present invention I claim as my invention:

1. An extrusion press comprising in combination: a frame comprising upper and lower horizontal slab members maintained vertically spaced apart by first and second vertical slab members interposed between and each disposed at one end of said frame, and connecting means for connecting the ends of each of said horizontal slab members to the ends of each of said vertical slab members in shear sustaining relation, said frame being closed at its top and bottom and at each of its ends but open at its opposite sides; an extrusion die connected to said first vertical slab member in such manner that the first vertical slab member will resist horizontal displacement of said die; a billet container positioned adjacent to said extrusion die; a piston and cylinder means projecting horizontally from said second vertical slab member and including a ram supported on the free end of the piston and adapted to enter the billet cntainer during extrusion of a billet; and means for communicating hydraulic fluid under pressure into said piston and cylinder means for forcibly displacing said ram into said billet container; an expansive force being created during extrusion of a billet which tends to separate said first and second vertical slab members; said connecting means resisting substantially all of said expansive force.

2. The combination of claim 1 wherein said upper and lower horizontal slab members each comprise a substantially unmachined, steel slab.

3. The combination of claim 1 wherein each of said connecting means comprises a shear key and at least one keyway formed in one of said slab members, said key and keyway extending transversely of said horizontal slabs.

4. The combination of claim 1 wherein each of said connecting means comprises an extrinsic shear key and complementary keyways formed in the engaged ends of said horizontal and vertical slab members; said complementary keyways extends transversely of said upper and lower horizontal slab members.

5. The combination of claim 1 wherein each of said connecting means comprises a rib member serving as a shear key and forming an integral part of one of said members and a keyway formed in the other of said members; said rib member residing within said keyway and extending transversely of said upper and lower slab members.

6. The combination of claim 1 wherein each of said connecting means comprises an end portion of said vertical slab member residing within a slot formed in said horizontal slab member.

7. The combination of claim 1 wherein the width of each of said first and second vertical slab members is substantially equal to the width of said upper and lower horizontal slab members.

8. The combination of claim 1 including carrier means supporting said ram; means slideably connecting said carrier means to the free end of said piston means for movement between a first position wherein said ram is axially aligned with the central axis of said extrusion die to a second position wherein said ram is disposed outward of said frame; and ram motor means for moving said carrier means from said first position to said second position and vice versa.

9. The combination of claim 8 wherein said ram motor means comprises a hydraulically operated piston and cylinder means, said piston being movable into coupled engagement with said carrier means.

10. The combination of claim 8 including carriage means for supporting said ram motor means in a horizontal position; vertically oriented pivot means at one end of said carriage means, said carriage being movable in a gate-like fashion from an operative position wherein said ram motor means is positioned normal to said ram, to an inoperative position which is angularly spaced from said operative position; and track means associated with the other end of said carriage means for guiding said carriage means during its gate-like movement.

11. The combination of claim 1 wherein said piston and cylinder means comprises a first tubular member extending from said second vertical slab member and having only its inner surface machined; a second tubular member slideable within said first tubular member and having only the outer surface thereof machined; and means for sealing the projecting end of said second tubular member; said hydraulic fluid under pressure being communicated to the interiors of said first and second tubular members for moving the ram toward said billet container.

12. The combination of claim 11 wherein said second tubular member has an outside diameter which is less than the inside diameter of said first tubular member; and means disposed in the annular space between said first and second tubular members for supporting said second tubular member during movement thereof.

13. The combination of claim 1 including first track means upon which said billet container is slideable toward and away from said extrusion die; platform means supporting said first track means; second track means supporting said platform means for movement transversely of said first track means; container motor means releasably connected to said billet container for moving the same from an operative position adjacent to said extrusion die to an inoperative position spaced therefrom and vice versa; and platform motor means connected to said platform means for moving said platform and said billet container from said inoperative position to a position outboard of said frame and vice versa.

14. The combination of claim 13 wherein said first motor means comprises a hydraulically operated piston and cylinder having a limited stroke whereby movement of said billet container away from said extrusion die is limited to a position wherein said billet container is generally centered over said second track means.

15. The combination of claim 13 including means for guiding said billet container during its movement over said platform, said means comprising a pair of wear plate members and a vertical bearing member interposed between and engaged by said wear plate members; one of said members being secured to said platform and the other of said members being secured to said billet container.

16. The combination of claim 15 including adjustment means supporting each of said wear plates for movement transversely of said platform, said billet container being displaceable transversely of said press frame by said adjustment means to compensate for horizontal misalignments between the central axis of a billet receiving opening in said billet container and the central axis of said extrusion die.

17. The combination of claim 13 wherein said first track means comprises spaced-apart wear plates secured to and extending over said platform; each of said wear plates being inclined with its inboard edge spaced upwardly from said platform; and including a pair of cooperating shoe members interposed between each wear plate and the underside of said billet container; means disposed between said shoe members permitting independent angular displacement of the upper shoe member whereby the lower shoe member is disposed at all times in overall surface contact with said Wear plate.

18. The combination of claim 17 wherein the lower shoe member is slideable over the Wear plate and the upper shoe member is slideable over the underside of said billet container; and including means for displacing each pair of cooperating shoe members transversely of said press frame for compensating for vertical misalignments between the central axis of a billet receiving opening in said billet container and the central axis of said extrusion die.

19. The combination of claim 13 including stop means for terminating the movement of said platform when said billet container is disposed in said inoperative position; said stop means comprising at least two block members, one each secured to said platform means and to said lower horizontal slab; one of said block members having a generally V-shaped groove formed therein which opens toward the outboard position of said billet container; and a generally V-shaped plate portion projecting from the other of said block members; said generally V-shaped plate portion being received in said groove to terminate the movement of said platform means.

20. The combination of claim 13 including a billet loading mechanism comprising a carriage supported on one side of said upper horizontal slab for movement parallel with the movement of said billet container; a swing frame suspended from said carriage, said swing frame being movable in a direction transversely of said press frame; a cradle supported at the lower end of said swing frame for swinging movement from an unloading position wherein the billet carried thereby is axially -aligned with the central axis of said die and positioned for loading into said billet container to a loading position which is outboard of said press frame; said swing frame maintaining said cradle means generally horizontal at all times; motor means for moving said cradle means between said unloading and loading positions; and means connecting said carriage to said billet container for movement therewith in a direction parallel to the central axis of said extrusion die.

21. The combination of claim 20 wherein said means for connecting said carriage to said billet container comprises a tongue and groove connection wherein said tongue is separable from said groove upon movement of said billet container from said inoperative position to the position outboard of said frame and wherein said tongue is engageable with said groove upon movement of said billet container from its position outboard of said frame to said inoperative position.

22. The combination of clam 1 including means supporting said billet container for movement toward and away fro msaid extrusion die; means for moving said billet container to an inoperative position which is spaced from said extrusion die upon completion of the extrusion of a billet; shear means carried on said upper horizontal slab member which is lowered through the space between said extrusion die and said billet container for shearing the butt and dummy of a billet just extruded; catch means normally disposed outboard of said frame for catching the butt and dummy block when sheared; swing arm means supporting said catch means and providing for swinging movement of said catch means from its normally outboard position to a position beneath the butt and dummy block; and motor means for swinging said catch means.

23. The combination of claim 1 including an extrusion die supporting assembly comprising a slide plate; first and second extrusion die assemblies, one each at each end of said slide plate; means supporting said slide plate for sliding movement transversely of said billet container; and motor means for moving said slide plate alternately from one position wherein said first extrusion die assembly is aligned with said billet container and said second extrusion die assembly is disposed outboard of said frame, to a second position wherein said second extrusion die assembly is aligned with said billet container and said first extrusion die assembly is disposed outboard of said frame.

24. The combination of claim 23 wherein said slide plate includes a well at each end thereof Within which said extrusion die assemblies reside; each of said extrusion die assemblies comprising a tool stack including a housing, a die plate disposed within said housing and adjacent to said billet container, and a backup plate disposed within said housing and adjacent to said die plate, said backup plate having an opening which is larger in diameter than the die opening of said die plate; and means for releasably securing said tool stack to said slide plate whereby said tool stack may be detached from said slide plate when each of said assemblies is disposed outboard of said frame.

25. The combination of claim 24 including die knockout means, one each on opposite sides of said frame for displacing the tool stack associated with said first and second extrusion die assemblies when each of said assemblies is disposed outboard of said frame, each of said die knockout means comprising a piston rod displaceable upwardly by means of hydraulic fluid, through an opening provided in said slide plate for engagement with said tool stack.

26. The combination of claim 25 wherein each of said extrusion die assemblies includes at least one bolster plate residing within said well and engaged with the face of said backup plate opposite said die plate, said bolster plate having an opening which is larger in diameter than the opening in said backup plate; and means for rigidly securing said bolster plate within said well whereby during the rim of the opening in said backup plate past the rim of the opening in said bolster plate.

27. In an extrusion press, the combination of a vertical slab member comprising a frame member; said vertical slab member having anopening therein through which an extrusion is discharged; an extrusion die assembly supported adjacent to said vertical slab member and comprising a slide plate; at least one extrusion die assembly supported on said slide plate; means supporting said slide plate for reciprocal movement transversely of said vertical slab member; motor means for moving said slide plate alternately from a first position wherein said extrusion die assembly is aligned with said opening and positioning for extrusion of a billet to a second position wherein said extrusion die assembly is positioned outboard of said vertical slab member; said extrusion die assembly comprising a die plate having a die opening for extrusion of a billet and a bolster plate having an opening which is larger in diameter than said die opening; said bolster plate being positioned relative to said vertical slab member with one face thereof engaged with and slideable over the inboard face of said vertical slab member whereby during movement of said slide plate'from said first position to said second position, any portion of said extrusion remaining within the opening of said bolster plate will be sheared.

28. In an extrusion press having a press frame, an extrusion die supported at one end of said press frame, and a billet container positioned adjacent to said extrusion die and adapted to receive and support a billet axially aligned with the central axis of said extrusion die, the combination comprising: cradle means for supporting said billet in a horizontal position; a swing frame suspended from said press frame and supporting said cradle means for swinging movement from an unloading position wherein the billet carried thereby is axially aligned with the central axis of said die and positioned for loading into said billet container to a loading position which is outboard or said frame, said swing frame maintaining said cradle means horizontal at all times; and motor means for moving said cradle means between said unloading and the loading positions.

' 29. The combination of claim 28 wherein said swing frame comprises pairs of spaced-apart, coplanar arms, one pair of arms at each end of said cradle means; each of said arms being pivotally connected at one end to said cradle means and pivotally connected at the other end to said frame; each said pair of arms comprising a pantograph structure which maintains said cradle means generally horizontal at all times.

References Cited UNITED STATES PATENTS 820,540 5/1906 Zimmerman 287-2092 1,037,213 9/1912 Derain 72253 1,250,841 12/1917 Gandell 28720.924 1,868,573 7/1932 Herman 287-20924 2,614,302 10/1952 Johnson 28720.92 2,720,970 10/1955 Roux 72263 2,728,453 12/1955 Thweatt 72263 2,938,706 5/1960 Langen 72239 2,941,665 6/1960 Weston 72257 3,025,959 3/ 1962 Poleschuk 72255 FOREIGN PATENTS 345,039 3/1931 Great Britain. 609,626 10/ 1948 Great Britain. 1,576,658 3/1964 Russia.

CHARLES W. LANHAM, Primary Examiner.

A. RUDERMAN, Assistant Examiner.

US. Cl. X.R. 72263 

